Turbine



March 5, 1946. R. w. YOUNGASH TURBINE Filed Feb. 17, 1942 4 Sheets-Sheet 1 March 5, 1946. R. w. YOUNGASH TURBINE Filed Feb. 17, 1942 ,4 Sheets-Sheet 2 12 711517701 I fisszmmmmmm March 5, 1946. w, YOUN ASH 2,396,068

TURBINE I Filed Feb; 17, 1942 4 Sheets-Sheet 3 a I J f V3! 9/ I;

w 29 46 92 L a/ March 5, 1946. R. w. YCUNGASH TURBINE 4 Sheets-Sheet 4 Filed Feb. 17, 1942 IN VENT UR IQEEINALU WILLIAM YUUNEASH ATTORNEY.

Patented Mar. 5, 1946 TURBINE Reginald William Youngash, Vancouver, British Columbia, Canada Application February 17, 1942, Serial No. 431,286 In Canada June 10, 1941 11 Claims.

This invention relates to turbines and particularly to air or combustion turbines.

An object of the present invention is the provision of a turbine which utilizes or converts into power a greater portion of the heat developed than has heretofore been achieved.

Another object is the provision of a turbine in which the blades are not subjected to damaging temperatures.

Another object is the provision of a turbine in which high temperatures are created and yet the structure of the turbine is protected against the extreme heat without diverting any or losing a great deal of the latter.

A further object is the provision of a turbine in which the bearings operate in comparatively cool air.

A still further object is the provision of a turbine including means for directing air under pressure thereto which will function efllciently despite changes in barometric pressure.

A further object is the provision of a turbine including efficient means for directing air under pressure thereto which provides for multiple compression stages without the necessity of airtight bearings between the stages for the prevention of pressure leakage.

Yet another object is the provision of a compact turbine unit of extremely simple construction and which is very small in comparison to its power output.

Many attempts have been made to produce hot air or combustion turbines but these have not been very successful for two principal reasons: (1) thermal inefliciency, and (2) the damage or destruction of the turbine blades, the combustion chamber, and other parts thereof by the extremely high temperatures involved.

In all internal combustion engines, such high temperatures are created that it is necessary to provide means for removing a substantial portion of the heat in order to protect the various parts of the engine, while a considerable amount of the heat passes through the engine as a surplus. In both cases, a large percentage of the heat is lost or wasted.

This invention overcomes these problems by introducing cool air into the hot air or gases being directed to the turbine blades in suflicient quarrtity to absorb and use the available heat. Suitable means is provided for rapidly and intimately mixing the hot and cool air and the expansion of the increased volume of air is converted into a forward movement. At the same time, at least some of the cool air is utilized to form a sheath increases the volume and decreases the temperature of the air being directed to the turbine blades, and it reduces the velocity of said air to a desired point.

Another advantage of this invention is that some or all the air to be directed to the turbine blades may, before being heated, be directed through and/or around the housing of the turbine to absorb any excess heat which may exist there. Furthermore, suitable means is provided for directing air to the unit which operates at maximum efficiency regardless of the barometric pressure of said air.

With the above and other objects in view, the present invention consists essentially of a turbine comprising a casing, a rotatable shaft extending through the casing, a plurality of turbine blades mounted on the shaft within the casing, a chamber, means for directing a stream of hot air under pressure through the chamber, means for introducing cool air into the hot stream, means for rapidly and intimately mixing the hot and cooler air, and means for directing the mixture to the turbine blades, as more fully described in the following specification and illustrated in the accompanying drawings, in which Figure l is a longitudinal section through a turbine illustrating one form of combustion chamber,

Figure 2 is an elevation of the forward end of the turbine, partly in section,

Figure 3 is a section taken substantially on the line 3-3 of Figure 1,

Figure 4 is a section taken on the line 4-4 of Figure 1, r

Figure 9 is an enlarged side elevation of a mixing nozzle,

Figure 10 is an end elevation of the mixing nozzle,

Figure ll. is a longitudinal section through an exhaust evacuator,

Figure 12 is a fragmentary sectional view of an alternative form of the invention,

Figure 13 is a reduced elevation of the turbine, with some parts omitted, showing an exhaust evacuator in position,

Figure 14 is a plan view, partly in section, of the nozzle tube shown in Figures 7 and 8,

Figure 15 is a view similar to Figure 9 with parts of the nozzle broken away, and

Figure 16 is an enlarged perspective view of the discharge end of the latter nozzle.

Referring more particularly to Figures 1 to i of the drawings, i5 is a casing having a rotatable shaft l6 extending therethrough, said casing having relatively large openings it and it in its opposite ends. A plurality of turbine blades 20 having stators 2i therebetween, are mounted on the shaft 66 in any suitable manner. While the blades 20 have been shown in multiple rows, it will be understood that a single row thereof may be employed. These blades are preferably mounted on a drum 22 which, in turn, is carried by a plurality of supporting blades 23 attached at their inner ends of a hub 26, fixedly mounted on the shaft It. The blades 23 may be twisted in the form of fan blades to direct air through the drum '22 or they may be flat, as shown. If desired, in the latter case, an inner deflector 25 may be r mounted on the inner endof the hub 2b with its periphery spaced from the drum 22, and an outer deflector as may be mounted on the outer end of the drum, the free edge of said outer deflector being substantially in line with the periphery of the outer deflector. The outer ends of the blades 23 may be formed with a plurality of small fan blades 271', so that the blades 23 and 2? form a V centrifugal fan within the drum, the purpose of which will hereinafter appear.

One or more elongated chambers 2e are provided through which hot air is directed towards the turbine blades 20 and for convenience only one of these chambers will now be described in detail.

A stream of hot air is directed under pressure through the chamber 28 and this stream may be generated outside or inside the chamber, preferably the latter, in any suitable manner.

The chamber tapers down at opposite ends to an inlet 29 and an outlet 30,- and at the inlet end, said chamber is formed with a cylindrical extension 3! which is preferably curved, as shown.

Atomized or vaporized fuel alone or fuel and air are supplied to the extension iii of the chamher by a fuel nozzle 32 connected by a pipe 33 to a suitable source of supply (not shown). Suitable means is provided for igniting the atomized or vaporized fuel in the chamber 28, a spark plug 34 being shown for this purpose in the drawings. In this way, a stream of hot air (the products of combustion) is directed through the chamber 28 centrally. thereof.

It fuel alone is injected into the chamber through the nozzle 32, it is necessary to mix air therewith before it reaches the spark plug 34. Air may be supplied to the outer end of the extension 3! in any suitable manner and a rapid mixture of the fuel and air is obtained by curving said extension, as shown.

vIt is preferable to form one or more sheat s 0f cool air around the stream of hot air in the chamber 28 to absorb heat therefrom to be utilized later and to protect the chamber and its associated elements from-the extremely high temperatures generated.

One way of accomplishing this is to supply cool air under pressure through the extension 3| to the chamber. One or more concentric Venturi tubes 35 which diverge from their inlet ends 36 towards their outlet ends 31, are mounted in the extension 3| and/or one or more similar and relatively long Venturi" tubes 38 are mounted in the chamber 28 at its inlet end and extend longitudinally thereof. If the extension 3! is curved, the tube or tubes 35 is or are similarly curved. Actually, the tube 38 may be a continuation of the tube 35 but it is preferable to have an opening therebetween at the inlet of the chamber. The nozzle 32 injects the fuel into the tube 35 and the spark plug 34 may project into the opening 49.

With this arrangement, the air passing through the tube 35 mixes with the fuel and the mixture is ignited by the spark plug, the curve of the tube assisting in the mixture' of'the fuel and air. If the tube 38 is provided, the flame and the stream of hot air are directed down this tube. The cool air around the outside of the tubes 35 and 38, or the combustion area, forms a protective sheath which absorbs heat from said area and protects these tubes and the chamber, while some of the cool air is drawn in through the opening 40 and passes through the tube 38 along its inner surface.

40 by the tapering of the outlet end of the chamber into the constricted outlet 38 where the intimate contact transfers some of the velocity and a proportionate part of the heat to the sheath air.

Suitable means is provided for converting the volume of air in thechamber 28 under pressure to velocity or forward movement at a lower pressure. In Figure 1, a constricted nozzle H is provided for this purpose. The nozzle extends outwardly from the constricted outlet 30 of the chamber and it is preferably curved, as shown. This nozzle expands the mixture after its passage through the constricted outlet forming said mixture into a high velocity jet. The constricted area and the curve of this nozzle assists in completel mixing the hot and cooler air from the chamber, and the curve reduces the possibility of any liquid fuel proceeding further in that state. This result is due to the fact that any liquid fuel, which would be very much heavier than the surrounding air, is smashed against the curved wall of the nozzle, thus being broken into minute particles. The expansion of the air at this point creates a further drop in temperature. The nozzle discharges into a pipe 42.

At this point, it is preferable to entrain more cool air with the stream of air from the chamber and this may be done in any suitable manner. In Figure 1, a shell 43 is concentric withand spaced from the chamber 28 to form a passage 44 therebetween. This shell, which preferably covers most of the chamber, opens out to the atmosphere outside the device at its entrance 45, or it may be connected to any suitable source of compressed air, and at its opposite end it tapers to a curved extension 46 surrounding the nozzle 4|, said extension being connected to the pipe 42. If compressed air is used, it may be supplied in any desired manner, such as, by means of a pipe I [5 extending from the fan casing 55 to the end of the shell 43, which is closed in this case, see Figure 12.

Another constricted nozzle 41 is movably mounted in the pipe 42 and it may be retained in any adjusted position in said tube in any suitable manner, such as by a set screw 48. The constriction 50 of this tube is spaced a little from its entrance and the tube diverges from the constriction to the opposite end thereof.

The constriction 50 is spaced from the end of the nozzle 4!. The jet from the nozzle entrains cooler air from the passage 44 in the shell 43. This air, entering the shell through the entrance 45, forms a protective sheath of cool air around the chamber 28 to absorb heat therefrom and protect it from the excessive heat generated 'therein. This causes the air in the passage to expand, acquiring some velocity, and this expanded air is mixed with the hot air of the jet. The constriction 50 causes a rapid and intimate mixture of the hot air from the lot and the cooler air from the passage 44. This air further mixes beyond the constriction in the tube 41 and it expands therein with a further drop in tempera.- ture. The tube 41 confines this greatly increased volume of air so that the expansion is converted into velocity or forward movement.

This air is now directed by the tube 41 and the pipe 42 into an annular intake passage 5| at the forward end of the casing I5, and this passage directs the air to the turbine blades 20. An annular exhaust passage 52 formed at the rearward end of the casing I5, receives the exhaust air from the turbine blades, and this air is removed from this chamber through one or more exhaust pipes 53, see Figure 2.

The pressure of the cool air supplied to the chamber 28 may be created in any desired manner. This is preferably done in the following manner:

A housing 54 extends from a point adjacent the rearward end of the drum 22 through and beyond the inner opening l8 of the casing l5. This housing converges from the casing l5 towards its outer end and it may be connected directly to the extension 3| of the chamber 28, or it may be connected to a fan'casing 55 which, in turn, is connected by a pipe 56 to said extension. The shaft 16 extends through the housing 54 and the casing 55.

One or more compression units 51 are mounted in said housing. Each unit consists of blades 58 projecting outwardly from a hub 59 mounted on the shaft l6, and stator blades 60 carried by the housing, mounted behind the blades 58.

If the fan casing 55 is provided, a centrifugal fan BI is mounted therein upon the shaft l6. This fan consists of flat blades 62, see Figures 1 and 3, projecting outwardly from a hub 63 and having a plurality of tangential blades 64 mounted on their outer ends in suitable manner, such as by means of spaced annular plates 65 located on each side of the blades, said plates being mounted on the outer ends of the blades 62.

A collector ring 63 is removably mounted in the casing 55 around the centrifugal fan 6|. This ring has a plurality of tangential tapered passages 61 formed therein which lie on the opposite tangent to that of the blades 64 of the fan 3 I.

A constricted tube 68 is movably mounted in the pipe 58 and it may be retained in any desired position by a set screw 10. This tube has a constriction I l adjacent its outlet end.

While one or more compression units 51, a centrifugal fan BI, and a. centrifugal or ordinary fan arrangement in the drum 22, have been described, any one or any combination of these may be employed. With this compression arrangement, the air is compressed in multiple stages and by screw and centrifugal fans. The combination of these two types of fan has the effect of securing a more constant output of air at varying barometric pressures. The efliciency of the screw type fan depends chiefly on the velocity of the air through the blades, while the centrifugal type depends largely on the weight of the air. At sea level, the centrifugal fans will have their maximum efliciency while the screw blades are operating on a smaller volume of air than they are capable of moving, the loaded centrifugal fans forming a back pressure, but with a reduction of the barometric pressure, the load of the centrifugal fans is reduced, thus allowing the screw blades to increase their volumetric efficiency to compensate for the loss in the centrifugal fans.

A preferred form of exhaust evacuator is illustrated in Figure 11. This evacuator consists of an elongated cylinder I4 and a pipe 15 extending from one of the exhaust pipes 53, see Figure 13, projects a short distance into said cylinder. A curvilinear tube 16 with a constriction 1'! at its forward end, extends longitudinally of the cylinder from a point adjacent the end of the pipe I5 through the opposite end of the cylinder. The curves of the tube 16 create a plurality of concave pockets 19 therein, and one or more orifices are formed in said tube at the bottom of each pocket.

The movement of the exhaust air through the tube 16 tends to form vacuums in the pockets 79 by drawing air therefrom so that air rushes into said pockets through the orifices from the space surrounding the tube. At the same time, the increase in the velocity of the air through the constriction TI sucks air into the tube from the surrounding area. Thus, by removing air from the cylinder 14, the movement of the exhaust air through the tube 16 lowers the pressure in said cylinder to a point below atmospheric pressure. The pipe 15 projects into the cylinder 14 and, consequently, the difference between the pressure of the air entering the chamber 28 and the pressure of the air into which the exhaust is discharged, is greater than if it were discharged directly into the atmosphere.

The general operation of the turbine is as follows:

Air entering the system through the hub of the turbine blades 20, assists in keeping the temperature of these blades down, it conserves the mechanical strength of the hub and said blades, and it protects the shaft l6 and its bearings from the heat. At the same time, the heat absorbed by this air is utilized later. The pressure of this air is increased by the centrifugal and ordinary fans described above and it is directed under pressure to the chamber 28. Some of this air is mixed with the fuel and burned in the tubes 35 and 38 while the remainder of the air forms a protective sheath around said tubes. The proportioning of the air through and around the tubes is regulated by moving the tube 68 along the pipe 56. As the constriction H is moved closer to the entrance of the tube 35, the

more air is directed through said tube. and as the constriction is moved away therefrom, the more is directed around the tube. The adjustment and size of the tubes 88 and i? regulates the pressure in th chamber 28.

The hot stream or air expands in the tube 33 and in the chamber 28 and it is mixed with the cooler air of the sheath therein. The expansion of this mixture is converted into velocity in the nozzle ii wherein further mixing and limited expansion takes place. Th sheath of air around the outside of the chamber 38 is entrained with the air from the nozzle and the two are mixed and expanded in the Venturi tube ll further to cool. the hot stream and to increase the volume or air which is constrained so that the velocity thereof is increased. This air is directed to the turbine blades 22 which rotate the shaft it. The exhaust air from the turbine blades passes through the exhaust evacuator 2 6 which func tions as described.

so is used to cool the various parts of the turblue and yet the heat absorbed by this air is returned to and utilized in the turbine. Cooler air is added to the hot stream both inside the chamber 28 and beyond said chamber but it is to be understood that this be done in either place or together, as shown.

An alternative form of chamber 213 is illustrated in Figure 5. In this case, another tube E li surrounds the tube 35 to divide the sheath of air around. the latter tube into two layers. The tube may or may not be used in this alternative but, in any event, a curvilinear tube is provided centrally of the chamber within the tube 33, it the latter is used. The tube has a plurality orifices round in the bottoms of the pockets created by the curve of tube. of air from the tube is directed through the tube 82 and as it must follow a tortuous passage therein, it is it imately .1 ed with the cooler air which has been through the opening and through the orifices The tube divides the surrounding sheath of cool air into layers.

The chamber converges to the constricted outlet 369, but in example the nozzle ll is formed on the forward end of the shell 63. The stream of hot air from the tube is rapidly and intimately mixed W1 .1 air of the surrounding sheath in the chamber and the jet of air be? therefrom entrains cooler air from the passage it and these are mixed expanded in the nozzle iii to convert the expansion into velocity. Another shell to surrounds at least a portion of the shell l3 forming a passage 85 therebetweeu. The shell 86 converges to a curved extension 36 which is connected to the pipe The tube ll is shown as being mounted in the extension '36 in stead of in the pipe :32, but it may be mounted in the latter, if desired.

The jet of air from the nozzle Si entrains cooler air from the passage to and these are intimately mixed and expanded in the tube ll. Here again, the air is cooled, and the velocity thereof in creased. This air directed to the turbine blades.

Figure 6 shows another alternative chamber 28. This chamber diverges slightly from its in let 29 and it has one or more constriction 8i formed therein with an opening 88 at each re= stricted point. The outlet to is larger in relation to the chamber than in the above alternatives but still constricted.

This form. of the invention may have only the tube 35 or it may also have the tube 8i and these all accuses tubes may be curved or they may be straight, as shown. The tube Bl may have an enlargement 90 adjacent its entrance, in which fuel from the nozzle 321s mixed with the compressed air entering the tubes 35 and 32. Either or both the tubes 38 and 82 may be located in the chamber and the latter tube may be straight, a shown. or it may be curvilinear as in Figure 5.

The shell is surrounds the chamber 28 and gradually converges to the extension d6 which is connected to the pipe 42. A curved nozzle 9G is mounted in the shell d3 adjacent the outlet end of the chamber 2B. The inlet end of this nozzle extends to the walls of the shell so that all of the hot air from the chamber and the cooler air from the passage it enters said nozzle. A plurality of orifices 9?. may be formed in the extension Qt adjacent the point where the nozzle 9i joins the shell 03. These orifices communicats with a passage surrounding the nozzle 96 and supply cool air {or mixing at the outlet of the nozzle ti The stream of hot air it expanded and mixed in the chamber with the cooler air of the surrounding sheaths. some of the air from the passage 3 3 is drawn into the chamber through the openings 63 while the remainder of the air from said passage is mixed with the air from the chamber in the nozzle iii. The air is mixed and exoanded in this nozzle and the jet therefrom draws in cooler air through the orifices 92 and the passage These streams or air are'mized and expanded in the tube 12 and then directed to the turbine blades.

Figures 7, 8 and 1% illustrate an adjustable nozzle tube of rectangular cross section which may be used in place of any of the Venturi tubes above described. consists of tube 35 having opposed sides projectirw forwardly there from. the other two opoosed sides being emitted at this point. A section having sides 38 is ioivotally mounted by means or" oivots on the end of the tube at one side thereof, while ar1 other section tilt having sides W2 is pivotally mounted by means of pivots we on the end of said tube at the opposite side thereof. The side of the sections Si and Jill overlap the sides of the tube and the sides of one section overlap the sides of the other.

As the sides of the lower section Mil are posi tioned inside the sides of the upper section the nozzle tube is adjusted to its smallest size when the sides W2 contact the top of the section 9?. To increase the size of the venturi, the sections may be spread apart as long as the sides thereof overlap the sides 96. The degree of expansion which may take place in the Veuturi tube is regulated, within certain limits, by regulating the sections ill and i ii i.

All enlarged view of a mixing nozzle which may be used in any or the alternatives or the invention is illustrated in Figures 9, 10, i5 and 16. This nozzle 685 consists of a cylindrical section tilt from which a plurality of internal radiating passages till extend forwardly, each of said passages converging to a relatively thin outlet M8 at the outlet end Hill of the nozzle. A. double ended cone iii is located in the outlet end lit centrally thereof and projects outwardly therefrom, as shown in Figures 9, 15 and 16. The spaces between the radial passages Hui form external ll-shaped passages iii in the outside of the nozzle. These passages are the same depth as the radial passage at the discharge end H0 cm the nozzle 82 is i but they become shallower and narrow towards the opposite end thereof.

This nozzle is always situated where the hot stream of air passes through it and cooler air passes around it. In Figure 12, the nozzle I has been substituted for the nozzle II at the discharge end of the chamber 28 of the alternative of Figure 1. The hot air from said chamber passes through the radial passages I01 and is divided into a plurality of thin radial streams passing out through the outlets I08. In this way, a very large surface of hot air comes into direct contact with the cooler air which is drawn or propelled through the passages I II from the passage 44. The cooler air flows from the passages H2 between the thin radial streams of hot air. Thus, a larger percentage of the cooler air comes into direct contact with the hot air than is the case with ordinary nozzles, such as the nozzle II. This ensures an extremely rapid and intimate mixing of the air and it also permits a larger quantity of cooler air to be mixed with the hot air with increased efficiency than otherwise possible.

Various modifications may be made in this invention without departing from the spirit thereof or the scope of the claims, and therefore, the exact forms shown are to be taken as illustrative only and not in a limiting sense, and it is desired that only such limitations shall be placed thereon as are set forth in the accompanying claims.

What I claim as my invention is:

1. In a turbine of the type described, having cooperating turbine and stator blades, means for supplying hot gases to the blades comprising, a chamber having an inlet and an outlet at opposite ends thereof, an inner tube in the inlet of the chamber, a constricted tube connected to the inlet of the chamber beyond the tube therein and having an outwardly flaring portion adjacent the end of said inner tube, means for supplying air to the chamber through the constricted tube, said constricted tube directing the air through and around the inner tube, means for igniting the fuel of the inner tube to form a stream of hot air flowing through the chamber centrally thereof, the cooler air in the chamber forming a sheath around the hot stream, means for intimately mixing the hot and cooler air in the chamber adjacent its outlet end, a nozzle extending outwardly from the outlet of the chamber forming a jet of the mixed air, means forming a sheath of cool air around the chamber, a second constricted tube with reversed tapered portions therein adapted to receive the jet from the nozzle, means for directing cooler air from the sheath to the jet at the entrance of the last mentioned tube, the mixture of hot and cooler air being expanded and the expansion converted to velocity in said tube, and means for directing the mixtur to the turbine blades.

2. A device according to claim 1, in which both constricted tubes are adjustable in relation to the chamber to regulate the pressure therein.

3. In a turbine of the character described, fluid supply means comprising an internally constricted nozzle adapted to efiect an increase in the velocity of the supply fluid, a fuel supply chamber having inlet and outlet tubes, the inlet tube being connected to the nozzle, a fuel supply tube of less diameter than the inlet tube and mounted within the same whereby the air supply will be divided into two concentric layers, means for supplying fuel to the inlet tube, means within the iuel supply chamber for dividing fuel flowing through the same into a plurality of concentric layers. an air supply tube surrounding the fuel chamber having a restricted outlet adjacent to the outlet of the fluid supply chamber and adapted to supply a layer of air around the fluid passing from the outlet, a constricted nozzle adjacent to the outlet of the fuel supply chamber.

4. In a turbine of the type described having cooperating turbine and stator blades, means for supplying hot gases to the blades, comprising an elongated chamber restricted at each end to form an imet at one end and an outlet at the other, an inlet tube extending outwardly from said inlet and an outlet tube extending outwardly from said outlet, means ior supplying air under pressure to the inlet tube, supply nozzle means mounted. in said imet tube and adapted to divide the incoming air into at least two concentric layers, a constricted nozzle mounted adjacent to the supply end of said supply nozzle means and adapted to receive said air under pressure and pass it to said inlet tube and said supply nozzle means, means for supplying such supply nozzle means with fuel to form with the innermost layer of air a combustibie mixture, means ior igniting such mixture to form a stream or hot gases no wing through said chamber centrally thereof, an open-ended tube mounted within said elongated chamber and adapted to receive such hot gases while the greater part or the remaining air passes around the exterior of said open-ended tube to form a cooling sheath, a nozzle formed with an internal constrictlon ad acent to the end of said outlet tube, and means for conducting the gases from the last mentioned nozzle to said blades.

5. In a turbine oi the type described having cooperating turbine and stator blades, means for supplying hot gases to the blades comprising an elongated chamber restricted at each end to term an inlet at one end and an outlet at the other, a curved inlet tube extending outwardly from said inlet and a curved outlet tube extending outwardly irom said outlet, means 101 supplying air under pressure to the inlet tube, supply nozzle means monted in said inlet tube and adapted to divide the incoming air into at least two concentric layers, a constricted nozzle adapted to receive said air under pressure and pass it to said inlet tube and supply nozzle means, said nozzle bein mounted adjacent to the supply end of said supply nozzle means and being movable towards and away therefrom to vary the amount of air in respective concentric layers, means for supplying such supply nozzle means with fuel to form with the innermost layer of air a combustible mixture, means for igniting such mixture to form a stream of hot gases flowing through said chamber contrally thereof, an open-ended tube mounted within said elongated chamber and adapted to receive such hot gases while the greater part of the remaining air passes around the exterior of said open-ended tube to form a cooling sheath, a nozzle formed with an internal constriction ad acent to the end of said curved outlet tube, and means for conducting the gases from the last mentioned nozzle to said blades.

6. In a turbine of the type described having cooperating turbine and stator blades, means for supplying hot gases to the blades comprising an elongated chamber restricted at each end to form an inlet at one end and an outlet at the other, a curved inlet tube extending outwardly from said inlet and a curved outlet tube extending outwardly from said outlet, means for supplying air under pressure to the inlet tube, supply nozzle means mounted in said inlet tube and adapted to divide 6 essence the incoming air into at ieest two concentric layers, a constricted nozzle adapted to receive said air under pressure anti pass it to said inlet tube and supply nozzle means, said nozzle being mounted adjacent to the supply end of Said supply nozzle means and being movable towards and away therefrom to vary the amount of air in respective concentric layers, means for supplying such supply nozzle means with iu'ei to form with the innermost layer of sit a combustible mixture, means for igniting such mixtme to form at stream of hot gases flowing through said chamber sen trally thereof, an open-ended tuhe mounted, with in said elongated chamber and ecletpteii to receive such hot gases while the greater part of the re maining ell passes around; the exterior oi sale open-ended tube to form e cooling sheath, opcn-ended tube increasing; in diameter towards the outlet of said elongated chamber, e, nozzle formed with on internal constriction. adjacent to the end of Sitiei curved outlet tube, eh sir supply tube surrounding soiol elongated chamber ens-l having one encl c ceo. to atmosphere and the othei encl constrictecl eclieccut to end. of said cutlet tube, the air space defined by the constricted end of said air supply tube surrounding the outlet tube of said eichgsteil chamber and communicat ins with the bore of the constricted nozzle ed iecent to seicl outlet whereby gee-es is said outlet tube are mixed ill. staid constricted nozzle with cooling size teem supply tube,

means for conducting the mixture from said constricted nozzle tube to said blades.

7. The turbine as claimed in claim 6 in which the open-ended tube mounted within the elongated chamber is formed with adjustable sections by means of which the rate of increase in its diameter msy be regulated.

8, The turbine as claimed in claim 5 in which said outlet tube is formed with a cylindrical ooz tion lieu/lug s, plurality of internal radiating pessages, each oi said passages converging to a relam tively thin slotdiiie outlet.

9. The turbine as claimed in claim 5 in which said outlet tube is formed with e cylindrical por time having it plurality of internal radiating passages, each of said passages converging to c, reietiveiy thin slotiike outlet end a centrally loceteti conical member extending outwardly in the clirection of flow oi the gases.

ill turbine es cit-timed in claim 5 in which means are provided for adjustingthe oi the open enciegi tube mouiiteci within the elon-= gemci chamber.

ii. The turbine as claimed. claim 5 in which the opeil ehcieoi tithe ifiilllviillfifiztl, the curved sections forming sockets points at which the tube is provided with openings through which air is from outside to, the inside oi the tube REGKNALD JVIL'LMADJE YOUNG QSH. 

